EP1647792A2 - Accumulator with an internal heat exchanger for an air-conditioning system - Google Patents
Accumulator with an internal heat exchanger for an air-conditioning system Download PDFInfo
- Publication number
- EP1647792A2 EP1647792A2 EP05021612A EP05021612A EP1647792A2 EP 1647792 A2 EP1647792 A2 EP 1647792A2 EP 05021612 A EP05021612 A EP 05021612A EP 05021612 A EP05021612 A EP 05021612A EP 1647792 A2 EP1647792 A2 EP 1647792A2
- Authority
- EP
- European Patent Office
- Prior art keywords
- heat exchanger
- accumulator
- pressure
- low
- housing
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
- 238000004378 air conditioning Methods 0.000 title claims abstract description 8
- 239000007788 liquid Substances 0.000 claims description 21
- 239000002826 coolant Substances 0.000 description 31
- 238000000034 method Methods 0.000 description 3
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 2
- 229910052782 aluminium Inorganic materials 0.000 description 2
- 239000004411 aluminium Substances 0.000 description 2
- 230000008901 benefit Effects 0.000 description 2
- 238000010276 construction Methods 0.000 description 2
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000002788 crimping Methods 0.000 description 1
- 238000001125 extrusion Methods 0.000 description 1
- 238000001746 injection moulding Methods 0.000 description 1
- 230000010354 integration Effects 0.000 description 1
- 239000000314 lubricant Substances 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 239000000463 material Substances 0.000 description 1
- 238000003825 pressing Methods 0.000 description 1
- 238000003466 welding Methods 0.000 description 1
Images
Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B40/00—Subcoolers, desuperheaters or superheaters
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B43/00—Arrangements for separating or purifying gases or liquids; Arrangements for vaporising the residuum of liquid refrigerant, e.g. by heat
- F25B43/006—Accumulators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/0041—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits for only one medium being tubes having parts touching each other or tubes assembled in panel form
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D7/00—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall
- F28D7/10—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically
- F28D7/103—Heat-exchange apparatus having stationary tubular conduit assemblies for both heat-exchange media, the media being in contact with different sides of a conduit wall the conduits being arranged one within the other, e.g. concentrically consisting of more than two coaxial conduits or modules of more than two coaxial conduits
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/42—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element
- F28F1/422—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being both outside and inside the tubular element with outside means integral with the tubular element and inside means integral with the tubular element
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2309/00—Gas cycle refrigeration machines
- F25B2309/06—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide
- F25B2309/061—Compression machines, plants or systems characterised by the refrigerant being carbon dioxide with cycle highest pressure above the supercritical pressure
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2400/00—General features or devices for refrigeration machines, plants or systems, combined heating and refrigeration systems or heat-pump systems, i.e. not limited to a particular subgroup of F25B
- F25B2400/05—Compression system with heat exchange between particular parts of the system
- F25B2400/051—Compression system with heat exchange between particular parts of the system between the accumulator and another part of the cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/18—Optimization, e.g. high integration of refrigeration components
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D21/00—Heat-exchange apparatus not covered by any of the groups F28D1/00 - F28D20/00
- F28D2021/0019—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for
- F28D2021/0068—Other heat exchangers for particular applications; Heat exchange systems not otherwise provided for for refrigerant cycles
- F28D2021/0073—Gas coolers
Definitions
- the invention relates to an accumulator for an air-conditioning system, specifically for use in motor vehicles, comprising a housing with an elongated tubular wall and an internal heat exchanger built into the housing. More specifically, the invention relates to an accumulator for an air-conditioning system with a coolant circulation that can run supercritically, e.g. a CO 2 vehicle air-conditioning system.
- a coolant circulation normally comprises a condenser, a liquefier, and expansion device, an internal heat exchanger and an evaporator.
- the invention provides an accumulator with an internal heat exchanger that can be manufactured cheaply, does not need much space to be built in, but nevertheless provides enough surface area for heat exchange in the coolant.
- this type of accumulator is envisaged to have an internal heat exchanger comprising a tubular structure with radially protruding ribs aligned coaxially with the wall of the housing. These ribs define a multitude of high-pressure or low-pressure lines, through which the coolant flows.
- the construction according to the invention allows the heat exchanger structure to be supported by the housing, so that the strength of the walls of this structure can be minimised.
- the heat exchanger structure, and specifically its profile only has to meet the requirements for heat conduction and transfer. This means that the walls do not have to be very strong, despite the high operating pressures; a larger surface area for the heat exchanging structure can then be made from the same amount of material.
- the heat exchanger structure according to the invention can be manufactured cheaply by extrusion techniques. Since the structure of the heat exchanger according to this invention does not need closed channels for the high pressure and/or low pressure lines - only the radially protruding ribs - this simplifies the manufacturing process considerably, and no cores are needed.
- the heat exchanger structure is a separate component that can be placed in the accumulator simply and very ergonomically (it is like a second wall) . No changes are required to the exterior housing of the accumulator, i.e. the exterior housing can be manufactured as a simple tube by a reliable process, and it will be stable under pressure.
- Arranging the heat exchanger structure between the housing wall and a liquid container within the housing is particularly advantageous.
- the heat exchanger structure should preferably comprise both inward-pointing and outward-pointing radial ribs, so that lines for the coolant on the high pressure side are formed on one side and for the low-pressure side on the other.
- FIG. 1 represents a first embodiment of an accumulator according to this invention.
- the accumulator has an aluminium housing 10 with an elongated tubular wall 12 that is 4 to 6mm thick.
- the housing 10 is closed off at its axial ends by an upper and lower end piece 14, 16 respectively.
- the end pieces 14, 16 are held in place by a combination of crimping one edge of the housing wall 12a and a tight fit, e.g. using a collar 12b (see the upper end piece, 14), or by a circlip 18 (see the lower end piece, 16) fitted into a recess in the housing. If necessary, an additional seal 20 can ensure a tight connection.
- the upper end piece 14 comprises a low-pressure inlet 22 and a high-pressure outlet 24; the lower end piece 16 comprises a high-pressure inlet 26 and a low-pressure outlet 28.
- a liquid container 30 has been placed to hold the liquid coolant.
- a tubular element 34 that is connected to the low-pressure inlet and points towards the wall 32 of the liquid container 30juts through the open upper end of the liquid container 30 and projects inside it.
- tubular aluminium heat exchanger structure 40 with longitudinal radial ribs 42, 44.
- the cross-sectional shape of these ribs can be seen in Figure 2, and in detail in Figure 3.
- the heat exchanger structure 40 is supported by the interior face of the housing wall 12 on its outward-facing radial ribs 42, thereby forming a multitude of axial high pressure lines 46.
- the inward-facing radial ribs 44 are positioned on the outside of the wall 32 of the liquid container 30 and thereby define a large number of axial low-pressure lines 48.
- the heat exchanger structure 40 with its protruding ribs 42, 44 extends in the axial direction from the upper end piece 14 to the lower end piece 16.
- the heat exchanger structure 40 is connected to the end pieces (14, 16) by elastic, deformable plastic seals 50, 52, which seal off the low pressure side from the high pressure side.
- the seals 50, 52 have a number of conical protrusions 54, corresponding in number to the interstitial spaces between the inward-facing ribs 44 of the heat exchanger structure 40. These are pressed into said interstitial spaces.
- an airtight connection between the seals 50, 52 and the heat exchanger structure 4 can also be created by friction welding, which generally gives a better tolerance.
- the heat exchanger structure 40 can also be directly involved in the injection moulding process of the seals 50, 52. In any event, the heat exchanger structure 40 and the seals 50, 52 can form a pre-assembled component.
- the airtight connection of the seals 50, 52 with the end pieces 14, 16 shown in detail in Figure 6 is formed by pressing the seals 50, 52 onto the end pieces 14, 16.
- the connection can also be manufactured or supported by a slanting protrusion of a side wall 56 of the end pieces 14, 16 and/or by an additional flexible ring seal 58.
- the coolant mostly comes out of the evaporator in vapour form, under low pressure (this is hereinafter referred to as low-pressure coolant). It is then passed via the low-pressure inlet 22 in the upper end piece 14 into the accumulator. The low-pressure coolant reaches the inside of the liquid container 30 via the tubular element 34.
- the tubular element 34 directs the low-pressure coolant tangentially onto the wall 32 of the liquid container 30, so that the liquid portion of the low-pressure coolant is deposited on the wall 32 and flows down into the lower collection area of the liquid container 30.
- the gaseous portion of the low-pressure coolant rises upwards and goes past the top edge 32a of the liquid container 30, into the low-pressure lines 48, which are defined by the inward-pointing radial ribs 44 of the heat exchanger structure 40 and the exterior of the wall 32 of the liquid container 30.
- the low-pressure coolant flows downwards into the first ring-shaped collection channel 60. This first collection channel is connected to the low-pressure outlet 28, through which the low-pressure coolant leaves the accumulator.
- high-pressure coolant coolant under high pressure coming from the coolant circuit's condenser (hereinafter referred to as high-pressure coolant) enters the accumulator from below, via the high-pressure inlet 26.
- the high-pressure coolant goes into the high-pressure lines 46, which are defined by the outward-facing radial ribs 42 and the interior side of the housing wall 12.
- the high-pressure coolant therefore flows upwards, in the opposite direction to the low-pressure coolant, on the other side of the heat exchanger structure 40.
- the large effective surfaces of the low-pressure and high-pressure lines 46, 48 ensure that an efficient exchange of heat between the high-pressure coolant and the low-pressure coolant takes place.
- the high-pressure coolant is collected in a second ring-shaped collection channel 62 and leaves the accumulator via the high-pressure outlet 24, which is connected to the second collection channel 62.
- Varying the numbers, the widths (in the radial direction) and the thickness (along the circumference) of the ribs 42, 44 of the heat exchanger structure 40 makes it possible to design the low-pressure and high-pressure lines 46, 48 to suit particular requirements. In particular, this allows the optimum ratio between the effective heat exchange surfaces in the heat exchanger structure 40 to be produced, on the low-pressure side and the high-pressure side.
- An example of a cross-sectional shape of the heat exchanger structure 40 that differs from the one in Figure 3 is shown in Figure 7.
- FIGs 8 and 9 Another alternative embodiment with respect to the cross-sectional design of the heat exchanger structure 4 is given in Figures 8 and 9. These have both the inward-facing and outward-facing protruding radial ribs 42, 44 defining the lines 48 for the low-pressure coolant.
- the high-pressure coolant is in this case passed through separated channels 64 formed in the central part of the heat exchanger structure 40 (see Fig. 9).
- these alternative embodiments comprise inlet chambers 66 in the housing wall 12 at the points where they meet the end pieces 14, 16 (see Fig. 8).
- Figure 10 shows a second embodiment of for an accumulator according to this invention.
- the components that correspond to those in the first alternative embodiment and have the same function have been indicated with the same references, despite any possible differences in the concrete form of said components, and they will not be described further.
- the end pieces 14, 16 that close off the housing 10 are in this case welded onto the housing 10.
- the diameter of the low-pressure inlet 22 increases as it goes downward, thereby acting as a diffuser.
- a structure (68) is envisaged consisting of a single piece together with the upper seal 50, forming an expansion antechamber 70 with exit holes 72.
- the diffuser and the expansion antechamber ensure that the incoming low-pressure coolant is slowed down.
- the arrangement and the diameter of the individual exit holes 72 are adjusted with respect to regions with and without dynamic pressure in such a way that a homogenous exit flow with a steady flow velocity is guaranteed across the entire floor area of the expansion antechamber 70 into the liquid container 30.
- the liquid container 30 consists of a single piece together with the lower seal 52. Otherwise, the operating principle of this embodiment is the same as that for the first embodiment described.
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- Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Geometry (AREA)
- Chemical & Material Sciences (AREA)
- Analytical Chemistry (AREA)
- Power Engineering (AREA)
- Air-Conditioning For Vehicles (AREA)
- Heat-Exchange Devices With Radiators And Conduit Assemblies (AREA)
- Compression-Type Refrigeration Machines With Reversible Cycles (AREA)
Abstract
Description
- The invention relates to an accumulator for an air-conditioning system, specifically for use in motor vehicles, comprising a housing with an elongated tubular wall and an internal heat exchanger built into the housing. More specifically, the invention relates to an accumulator for an air-conditioning system with a coolant circulation that can run supercritically, e.g. a CO2 vehicle air-conditioning system. As well as an accumulator, such a coolant circulation normally comprises a condenser, a liquefier, and expansion device, an internal heat exchanger and an evaporator.
- The integration of an internal heat exchanger into an accumulator is a known technique, for example in US 6 523 365 B2, which demonstrates this type of accumulator. The internal heat exchanger in this case essentially comprises a double spiral tube within the accumulator housing, through which both the high and low pressure coolant flows are passed in opposite directions. The disadvantage of this construction is above all that the heat exchanger requires a lot of room in the accumulator.
- The invention provides an accumulator with an internal heat exchanger that can be manufactured cheaply, does not need much space to be built in, but nevertheless provides enough surface area for heat exchange in the coolant.
- According to the invention, this type of accumulator is envisaged to have an internal heat exchanger comprising a tubular structure with radially protruding ribs aligned coaxially with the wall of the housing. These ribs define a multitude of high-pressure or low-pressure lines, through which the coolant flows. The construction according to the invention allows the heat exchanger structure to be supported by the housing, so that the strength of the walls of this structure can be minimised. The heat exchanger structure, and specifically its profile, only has to meet the requirements for heat conduction and transfer. This means that the walls do not have to be very strong, despite the high operating pressures; a larger surface area for the heat exchanging structure can then be made from the same amount of material. The heat exchanger structure according to the invention can be manufactured cheaply by extrusion techniques. Since the structure of the heat exchanger according to this invention does not need closed channels for the high pressure and/or low pressure lines - only the radially protruding ribs - this simplifies the manufacturing process considerably, and no cores are needed. The heat exchanger structure is a separate component that can be placed in the accumulator simply and very ergonomically (it is like a second wall) . No changes are required to the exterior housing of the accumulator, i.e. the exterior housing can be manufactured as a simple tube by a reliable process, and it will be stable under pressure.
- Arranging the heat exchanger structure between the housing wall and a liquid container within the housing is particularly advantageous.
- The heat exchanger structure should preferably comprise both inward-pointing and outward-pointing radial ribs, so that lines for the coolant on the high pressure side are formed on one side and for the low-pressure side on the other.
- The formation of flow lines enclosed in the cross-section can then easily be carried out, since the ribs are next to the housing wall and the liquid container respectively.
- Further characteristics and benefits of the invention can be seen from the preferred embodiments described below and with reference to the attached figures. The figures show:
- Figure 1: a longitudinal section of an accumulator according to the invention, according to a first embodiment;
- Figure 2: a cross-section along the line A-A in Figure 1;
- Figure 3: a detailed enlargement of the cross-section of the heat exchanger structure in Figure 2;
- Figure 4: a cross-section along the line B-B in Figure 1;
- Figure 5: a detailed enlargement of the cross-section of the heat exchanger structure and the seal from Figure 4;
- Figure 6: an enlargement of detail X in Figure 1;
- Figure 7: a detailed enlargement of the cross-section of a heat exchanger structure according to a first alternative embodiment;
- Figure 8: a simplified view corresponding to Figure 1 for an accumulator according to the invention, according to a second alternative embodiment of the heat exchanger structure;
- Figure 9: a detailed enlargement of the cross-section of the heat exchanger structure according to the second alternative embodiment; and
- Figure 10: a longitudinal section of an accumulator according to the invention, according to a second embodiment.
- Figure 1 represents a first embodiment of an accumulator according to this invention. The accumulator has an
aluminium housing 10 with an elongatedtubular wall 12 that is 4 to 6mm thick. Thehousing 10 is closed off at its axial ends by an upper andlower end piece end pieces housing wall 12a and a tight fit, e.g. using acollar 12b (see the upper end piece, 14), or by a circlip 18 (see the lower end piece, 16) fitted into a recess in the housing. If necessary, anadditional seal 20 can ensure a tight connection. Theupper end piece 14 comprises a low-pressure inlet 22 and a high-pressure outlet 24; thelower end piece 16 comprises a high-pressure inlet 26 and a low-pressure outlet 28. - Between the two
end pieces liquid container 30 has been placed to hold the liquid coolant. Atubular element 34 that is connected to the low-pressure inlet and points towards thewall 32 of the liquid container 30juts through the open upper end of theliquid container 30 and projects inside it. At the lower end of theliquid container 30, there is anoutlet aperture 36 with afilter 38 in front of it, which is connected to the low-pressure outlet 28 so that small quantities of coolant and lubricant can exit through it. This avoids having oil accumulate in theliquid container 30. - Between the
tubular housing wall 12 and thewall 32 of theliquid container 30 there is a tubular aluminiumheat exchanger structure 40 with longitudinalradial ribs heat exchanger structure 40 is supported by the interior face of thehousing wall 12 on its outward-facingradial ribs 42, thereby forming a multitude of axialhigh pressure lines 46. The inward-facingradial ribs 44 are positioned on the outside of thewall 32 of theliquid container 30 and thereby define a large number of axial low-pressure lines 48. In total, theheat exchanger structure 40 with itsprotruding ribs upper end piece 14 to thelower end piece 16. - The
heat exchanger structure 40 is connected to the end pieces (14, 16) by elastic, deformableplastic seals seals conical protrusions 54, corresponding in number to the interstitial spaces between the inward-facingribs 44 of theheat exchanger structure 40. These are pressed into said interstitial spaces. Alternatively, an airtight connection between theseals seals 50, 52 - in this case without the protrusions 54 - onto the outer edge and then press them between theribs 44 of theheat exchanger structure 40. Finally, theheat exchanger structure 40 can also be directly involved in the injection moulding process of theseals heat exchanger structure 40 and theseals - The airtight connection of the
seals end pieces seals end pieces side wall 56 of theend pieces flexible ring seal 58. - In the following paragraphs, the operational principle of the accumulator in a typical coolant circuit for an air-conditioning system is described. The coolant mostly comes out of the evaporator in vapour form, under low pressure (this is hereinafter referred to as low-pressure coolant). It is then passed via the low-
pressure inlet 22 in theupper end piece 14 into the accumulator. The low-pressure coolant reaches the inside of theliquid container 30 via thetubular element 34. Thetubular element 34 directs the low-pressure coolant tangentially onto thewall 32 of theliquid container 30, so that the liquid portion of the low-pressure coolant is deposited on thewall 32 and flows down into the lower collection area of theliquid container 30. The gaseous portion of the low-pressure coolant, now separated from the liquid portion, rises upwards and goes past thetop edge 32a of theliquid container 30, into the low-pressure lines 48, which are defined by the inward-pointingradial ribs 44 of theheat exchanger structure 40 and the exterior of thewall 32 of theliquid container 30. The low-pressure coolant flows downwards into the first ring-shaped collection channel 60. This first collection channel is connected to the low-pressure outlet 28, through which the low-pressure coolant leaves the accumulator. - At the same time, coolant under high pressure coming from the coolant circuit's condenser (hereinafter referred to as high-pressure coolant) enters the accumulator from below, via the high-
pressure inlet 26. The high-pressure coolant goes into the high-pressure lines 46, which are defined by the outward-facingradial ribs 42 and the interior side of thehousing wall 12. The high-pressure coolant therefore flows upwards, in the opposite direction to the low-pressure coolant, on the other side of theheat exchanger structure 40. The large effective surfaces of the low-pressure and high-pressure lines collection channel 62 and leaves the accumulator via the high-pressure outlet 24, which is connected to thesecond collection channel 62. - Varying the numbers, the widths (in the radial direction) and the thickness (along the circumference) of the
ribs heat exchanger structure 40 makes it possible to design the low-pressure and high-pressure lines heat exchanger structure 40 to be produced, on the low-pressure side and the high-pressure side. An example of a cross-sectional shape of theheat exchanger structure 40 that differs from the one in Figure 3 is shown in Figure 7. - Another alternative embodiment with respect to the cross-sectional design of the heat exchanger structure 4 is given in Figures 8 and 9. These have both the inward-facing and outward-facing protruding
radial ribs lines 48 for the low-pressure coolant. The high-pressure coolant is in this case passed through separatedchannels 64 formed in the central part of the heat exchanger structure 40 (see Fig. 9). In order to allow the low-pressure coolant to enter the outer low-pressure lines 48 as well, these alternative embodiments compriseinlet chambers 66 in thehousing wall 12 at the points where they meet theend pieces 14, 16 (see Fig. 8). - Figure 10 shows a second embodiment of for an accumulator according to this invention. The components that correspond to those in the first alternative embodiment and have the same function have been indicated with the same references, despite any possible differences in the concrete form of said components, and they will not be described further.
- The
end pieces housing 10 are in this case welded onto thehousing 10. The diameter of the low-pressure inlet 22 increases as it goes downward, thereby acting as a diffuser. Instead of thetubular element 34, a structure (68) is envisaged consisting of a single piece together with theupper seal 50, forming anexpansion antechamber 70 with exit holes 72. The diffuser and the expansion antechamber ensure that the incoming low-pressure coolant is slowed down. The arrangement and the diameter of the individual exit holes 72 are adjusted with respect to regions with and without dynamic pressure in such a way that a homogenous exit flow with a steady flow velocity is guaranteed across the entire floor area of theexpansion antechamber 70 into theliquid container 30. In this embodiment, theliquid container 30 consists of a single piece together with thelower seal 52. Otherwise, the operating principle of this embodiment is the same as that for the first embodiment described. - It is naturally possible to apply certain features of one embodiment or alternative embodiment to another embodiment or alternative embodiment.
- All the embodiments and alternative embodiments described are characterised in that a stable and easily produced tube with a wall up to 6mm thick can be used as the
housing 10, so that theheat exchanger structure 40 stabilised by thehousing wall 12 can be made with a lower wall strength. This cost-effective design enables a very large heat exchange surface to be made in a small volume and at a low weight, which is a major advantage for a supercritical CO2 coolant circuit at high pressures (operating pressure on the high pressure side up to 140 bar; the pressure on the low-pressure side when the air-conditioning unit is switched off is up to 100 bar).
Claims (11)
- An accumulator for an air conditioning system, including a housing (10) with an elongated tubular wall (12) and an internal heat exchanger fitted in the housing (10), characterised in that the internal heat exchanger has a tubular structure (40) with radially protruding ribs (40, 42) arranged coaxially with the housing wall (12).
- An accumulator according to claim 1, characterised in that the heat exchanger structure (40) comprises radial ribs pointing both inwards and outwards (42 and 44 respectively).
- An accumulator as per Claim 2, characterised in that the heat exchanger structure (40) is placed between the housing wall (12) and a liquid container (30) that is fitted inside the casing (10).
- An accumulator according to claim 3, characterised in that the ribs (42, 44) adjoin the housing wall (12) and the liquid container (30) respectively.
- An accumulator according to any of claims 2 to 4, characterised in that the interstitial spaces between the inward-pointing radial ribs (44) are connected to a low-pressure inlet (22) of the accumulator.
- An accumulator according to claim 5, characterised in that the interstitial spaces between the outward-pointing radial ribs (42) are connected to the low-pressure inlet (22).
- An accumulator according to any of claims 2 to 5, characterised in that the interstitial spaces between the outward-pointing radial ribs (42) are connected to a high-pressure inlet (26) of the accumulator.
- An accumulator according to any of the above claims, characterised in that channels (64) have been formed in a central region of the heat exchanger structure (40).
- An accumulator according to any of the above claims, characterised in that seals (50, 52) have been fitted to both axial ends of the heat exchanger structure (40) and that the heat exchanger structure (40) and the seals (50, 52) form a pre-assembled component.
- An accumulator according to claim 9, characterised in that the seals (50, 52) are connected to the end pieces (14, 16) that close off the axial ends of the housing (10).
- An accumulator according to claim 10, characterised in that a low-pressure inlet (22) and a high-pressure outlet (24) are formed in one end piece (14), and a high-pressure inlet (26) and a low-pressure outlet (28) in the other end piece (16).
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PL05021612T PL1647792T3 (en) | 2004-10-15 | 2005-10-04 | Accumulator with an internal heat exchanger for an air-conditioning system |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE102004050409A DE102004050409A1 (en) | 2004-10-15 | 2004-10-15 | Accumulator with internal heat exchanger for air conditioning |
Publications (3)
Publication Number | Publication Date |
---|---|
EP1647792A2 true EP1647792A2 (en) | 2006-04-19 |
EP1647792A3 EP1647792A3 (en) | 2006-06-28 |
EP1647792B1 EP1647792B1 (en) | 2011-07-13 |
Family
ID=35717639
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
EP05021612A Active EP1647792B1 (en) | 2004-10-15 | 2005-10-04 | Accumulator with an internal heat exchanger for an air-conditioning system |
Country Status (7)
Country | Link |
---|---|
US (1) | US7152427B2 (en) |
EP (1) | EP1647792B1 (en) |
JP (1) | JP5350578B2 (en) |
AT (1) | ATE516474T1 (en) |
DE (1) | DE102004050409A1 (en) |
ES (1) | ES2369141T3 (en) |
PL (1) | PL1647792T3 (en) |
Cited By (6)
Publication number | Priority date | Publication date | Assignee | Title |
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DE102005056651A1 (en) * | 2005-11-25 | 2007-05-31 | Behr Gmbh & Co. Kg | Coaxial tube or tube-in-tube arrangement, in particular for a heat exchanger |
FR2930018A1 (en) * | 2008-04-15 | 2009-10-16 | Valeo Systemes Thermiques | COMBINED DEVICE COMPRISING AN INTERNAL HEAT EXCHANGER AND AN ACCUMULATOR. |
ITTO20080568A1 (en) * | 2008-07-23 | 2010-01-24 | Dayco Fluid Technologies Spa | ADDUCTION GROUP FOR A CONDITIONED AIR CIRCUIT WITH A HEAT EXCHANGER |
CN110857823A (en) * | 2018-08-23 | 2020-03-03 | 杭州三花研究院有限公司 | Gas-liquid separator, air conditioning system, and method for manufacturing gas-liquid separator |
US11892212B2 (en) | 2018-08-23 | 2024-02-06 | Zhejiang Sanhua Intelligent Controls Co., Ltd. | Gas-liquid separator and air conditioning system |
EP4368932A1 (en) * | 2022-11-14 | 2024-05-15 | Danfoss A/S | Tank casing for refrigerant receiver with integrated heat exchanger functionality |
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DE102006035784B4 (en) * | 2006-08-01 | 2020-12-17 | Gea Refrigeration Germany Gmbh | Refrigeration system for transcritical operation with economiser and low pressure collector |
KR101300556B1 (en) * | 2007-01-24 | 2013-09-03 | 한라비스테온공조 주식회사 | Heat exchanger with accumulator of air conditioning system for automotive vehicles |
DE102007039753B4 (en) * | 2007-08-17 | 2017-12-21 | Hanon Systems | Refrigerant accumulator for motor vehicle air conditioners |
US20110174014A1 (en) * | 2008-10-01 | 2011-07-21 | Carrier Corporation | Liquid vapor separation in transcritical refrigerant cycle |
FR2940419B1 (en) * | 2008-12-22 | 2010-12-31 | Valeo Systemes Thermiques | COMBINED DEVICE COMPRISING AN INTERNAL HEAT EXCHANGER AND AN ACCUMULATOR, AND PROVIDED WITH A MULTIFUNCTIONAL INTERNAL COMPONENT |
FR2940420B1 (en) * | 2008-12-22 | 2010-12-31 | Valeo Systemes Thermiques | COMBINED DEVICE COMPRISING AN INTERNAL HEAT EXCHANGER AND AN ACCUMULATOR COMPRISING A CLIMATEING MOUTH |
FR2940418B1 (en) * | 2008-12-22 | 2012-12-07 | Valeo Systemes Thermiques | COMBINED DEVICE COMPRISING AN INTERNAL HEAT EXCHANGER AND AN ACCUMULATOR |
US9046289B2 (en) | 2012-04-10 | 2015-06-02 | Thermo King Corporation | Refrigeration system |
US9482445B2 (en) * | 2012-09-06 | 2016-11-01 | Jiangsu Tenesun Electrical Appliance Co., Ltd. | Heat pump water heater with heat utilization balance processor and heat utilization balance processor thereof |
DE102014220401A1 (en) * | 2014-10-08 | 2016-04-14 | Mahle International Gmbh | Refrigerant container for a refrigeration system |
DE102016201395A1 (en) * | 2016-01-29 | 2017-08-03 | Mahle International Gmbh | Method for producing a heat exchanger device |
JP2017219212A (en) * | 2016-06-03 | 2017-12-14 | サンデンホールディングス株式会社 | Internal heat exchanger integral type accumulator and freezing cycle using the accumulator |
JP6813373B2 (en) | 2017-01-20 | 2021-01-13 | サンデンホールディングス株式会社 | Accumulator with internal heat exchanger and refrigeration cycle equipped with it |
DE102022201431A1 (en) | 2022-02-11 | 2023-08-17 | Mahle International Gmbh | Collector for a refrigerant circuit |
Citations (1)
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US6523365B2 (en) | 2000-12-29 | 2003-02-25 | Visteon Global Technologies, Inc. | Accumulator with internal heat exchanger |
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DE3532930C1 (en) * | 1985-09-14 | 1986-05-28 | Norsk Hydro A.S., Oslo | Cooler, especially an oil cooler |
BR8604382A (en) * | 1985-09-14 | 1987-05-12 | Norsk Hydro As | FLUID COOLER |
JPS6361682U (en) * | 1986-10-07 | 1988-04-23 | ||
DE19903833A1 (en) * | 1999-02-01 | 2000-08-03 | Behr Gmbh & Co | Integrated collector heat exchanger assembly |
JP2001124442A (en) * | 1999-10-27 | 2001-05-11 | Mitsubishi Electric Corp | Accumulation receiver and its manufacturing method |
CA2297598C (en) * | 2000-01-28 | 2003-12-23 | Ki-Sun Jason Ryu | Accumulator for an air-conditioning system |
US6463757B1 (en) * | 2001-05-24 | 2002-10-15 | Halla Climate Controls Canada, Inc. | Internal heat exchanger accumulator |
JP4126408B2 (en) * | 2002-09-05 | 2008-07-30 | 株式会社ヴァレオサーマルシステムズ | Accumulator and refrigeration cycle using the same |
DE10348141B3 (en) * | 2003-10-09 | 2005-02-03 | Visteon Global Technologies, Inc., Dearborn | Inner heat exchanger for high pressure cooling medium providing dual function as accumulator and cooling medium collector |
-
2004
- 2004-10-15 DE DE102004050409A patent/DE102004050409A1/en not_active Withdrawn
-
2005
- 2005-10-04 AT AT05021612T patent/ATE516474T1/en not_active IP Right Cessation
- 2005-10-04 PL PL05021612T patent/PL1647792T3/en unknown
- 2005-10-04 ES ES05021612T patent/ES2369141T3/en active Active
- 2005-10-04 EP EP05021612A patent/EP1647792B1/en active Active
- 2005-10-11 US US11/247,802 patent/US7152427B2/en active Active
- 2005-10-14 JP JP2005299503A patent/JP5350578B2/en not_active Expired - Fee Related
Patent Citations (1)
Publication number | Priority date | Publication date | Assignee | Title |
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US6523365B2 (en) | 2000-12-29 | 2003-02-25 | Visteon Global Technologies, Inc. | Accumulator with internal heat exchanger |
Cited By (10)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005056651A1 (en) * | 2005-11-25 | 2007-05-31 | Behr Gmbh & Co. Kg | Coaxial tube or tube-in-tube arrangement, in particular for a heat exchanger |
FR2930018A1 (en) * | 2008-04-15 | 2009-10-16 | Valeo Systemes Thermiques | COMBINED DEVICE COMPRISING AN INTERNAL HEAT EXCHANGER AND AN ACCUMULATOR. |
EP2110624A1 (en) * | 2008-04-15 | 2009-10-21 | Valeo Systèmes Thermiques | Combined device comprising an internal heat exchanger and an accumulator |
ITTO20080568A1 (en) * | 2008-07-23 | 2010-01-24 | Dayco Fluid Technologies Spa | ADDUCTION GROUP FOR A CONDITIONED AIR CIRCUIT WITH A HEAT EXCHANGER |
WO2010010450A1 (en) * | 2008-07-23 | 2010-01-28 | Dytech - Dynamic Fluid Technologies S.P.A. | Fluidic assembly for an air conditioning circuit with a heat exchanger |
CN110857823A (en) * | 2018-08-23 | 2020-03-03 | 杭州三花研究院有限公司 | Gas-liquid separator, air conditioning system, and method for manufacturing gas-liquid separator |
CN110857823B (en) * | 2018-08-23 | 2020-11-06 | 杭州三花研究院有限公司 | Gas-liquid separator, air conditioning system, and method for manufacturing gas-liquid separator |
US11892212B2 (en) | 2018-08-23 | 2024-02-06 | Zhejiang Sanhua Intelligent Controls Co., Ltd. | Gas-liquid separator and air conditioning system |
EP4368932A1 (en) * | 2022-11-14 | 2024-05-15 | Danfoss A/S | Tank casing for refrigerant receiver with integrated heat exchanger functionality |
WO2024104798A1 (en) * | 2022-11-14 | 2024-05-23 | Danfoss A/S | Tank casing for refrigerant receiver with integrated heat exchanger functionality |
Also Published As
Publication number | Publication date |
---|---|
ES2369141T3 (en) | 2011-11-25 |
JP2006112778A (en) | 2006-04-27 |
EP1647792A3 (en) | 2006-06-28 |
US20060080997A1 (en) | 2006-04-20 |
EP1647792B1 (en) | 2011-07-13 |
US7152427B2 (en) | 2006-12-26 |
ATE516474T1 (en) | 2011-07-15 |
PL1647792T3 (en) | 2012-01-31 |
DE102004050409A1 (en) | 2006-04-27 |
JP5350578B2 (en) | 2013-11-27 |
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